Centrifugal Pumps Design and Application 2nd ed - Val S. Lobanoff, Robert R. Ross (Butterworth-Heinemann, 1992)

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Mechanical Seals 395 The measured leakage from each end of this horizontal pump was 10 to 120 ppm. This installation is a rotating seal head with a tungsten carbide insert running on a silicon carbide mating ring. A steam quench is being used on the atmospheric side of the seal. Hydropads are also used to aid the lubrication process on the refinery application shown in Figure 17-32. The pump is used in a hydrofluoric alkylation unit to move hydrofluoric acid. To protect the sealing system, a clean injection of isobutane is flushed in at the seal faces. The original seals experienced short seal life due to chemical attack from the hydrofluoric acid. The operating conditions for this application are: • Liquid sealed: isobutane/hydrofluoric acid » Stuffing box pressure: 240 psig • Temperature: 89°F • Specific gravity: 0,945 • Speed: llSOrpm » Seal size: 3.5 inches This hydropadded seal has added years to the service life of the unit, The materials of construction for the seal faces are solid silicon carbide running on solid silicon carbide. This material combination was selected for its excellent corrosion resistance to hydrofluoric acid, because corrosion is a common cause for seal failure on these types of applications. Hydropads or lubrication recesses when properly applied will result in improved seal life. This design feature is the first step in the process of advancement to non-contacting seals. Figure 17-32. Mechanical seal installation for refinery HF Alkylation Unit (courtesy John Crane).
396 Centrifugal Pumps: Design and Application True non-contacting seals are being applied to pumping equipment and will change the way a seal is viewed for a given application. When pumping a light hydrocarbon near its vapor pressure, it is more efficient to allow the liquid to flash to a gas in the stuffing box and use a dry running seal to seal the gas. This is done with a non-contacting seal design. This most efficient method in achieving non-contact in operation is through the use of the spiral groove face seal. This patented concept was developed by John Crane Inc. for use in sealing high performance gas compressors and is illustrated in Figure 17-33. The spiral groove pattern is a series of logarithmic spirals recessed into the hard mating ring. The ungrooved portion of the seal face below the spiral is called the sealing dam. The spiral groove pattern is designed to rotate only in one direction. As the seal face begins to rotate from the outside diameter of the seal faces to the groove diameter, gas is compressed and then expanded across the sealing dam. This will generate sufficient opening force to separate the seal faces by a few micro-inches. Seal balance, face width and spiral groove diameters are all critical and determine the static and dynamic operation of the seal during periods of startup and shutdown when the seal faces contact. A comparison of hydropadded and spiral groove faces is made in Figure 17-34, Figure 17-33. Dry running face design (courtesy of John Crane).
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CENTRIFIUGAL PUMPS Design & applica
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CENTRIFUGAL PUMPS Design & Applicat
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Contents Preface —..... —......
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ern Pumps, Mine Dewatering Pumps. W
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Stage Pumps. Single-Suction Single-
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Preface When Val and I decided to c
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CENTRIFUGAL PUMPS Design & applicat
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Part 1 Elements of Pump Design
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1 Introduction System Analysis for
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Introduction 5 Figure 1-2. The syst
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Introduction 7 mate responsibility
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Introduction 9 Figure 1-6. Maximum
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2 Specific Speed and Modeling Laws
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Specific Speed and Modeling Laws 13
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Figyre 2-7, New pump from model pum
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Impeller Design 29 Figure 3-1. Requ
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Impeller Design 31 Figure 3-4. Capa
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Impeller Design 33 Step 8: Estimate
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Impeller Design 35 Figure 3-7. Volu
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impeller Design 37 (2) 5 , as final
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Impeller Design 39 The vane develop
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Impeller Design 41 Figure 3-12. Are
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impeller Design 43 Figure 3-16. Inf
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4 General Pump Design It is not a d
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General Pump Design 4? Figure 4-1.
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General Pump Design 49 designed and
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Volute Design 51 Figure 5-1. Volute
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Volute Design 53 Figure 5-2. Radial
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Volute Design 55
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Volute Design 57 Figure 5-4. Effici
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Volute Design 59 Figure 5-5. Typica
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Volute Design 61 Figure 5-8. Univer
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Volute Design S3 Manufacturing Cons
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6 Design of Multi-Stage Casing Mult
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Design of Multi-Stage Casing 67 How
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Design of Multi-Stage Casing 69 Fig
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Design of Multi-Stage Casing 73 sec
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7 Double-Suction Pumps and Side-Suc
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Double-Suction Pumps 79 two. Experi
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Double-Suction Pumps 81 Figure 7-3.
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Double-Suction Pumps 83 LOCATION AR
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8 NPSH The expressions NPSHR and NP
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NPSH 87 Predicting NPSHR The other
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NPSH 89 Figure 8-4. Pressure loss b
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NPSH 91 SUCTION VELOCITY TRIANGLES
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NPSH 93 Figure 8-8. Performance cur
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NPSH 95 Figure 8-10. Leakage across
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NPSH 97 Figure 8-13. Plate inserts
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NPSH 99 Figure 8-17. Influence of p
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NPSH 101 Figure 8-19. Estimating K
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NPSH 103 Step 3: Determine KI* From
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Figure 8«22. Calculating NPSHA for
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NPSH 107 Figure 8-24. NPSHR cavitat
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NPSH 109 Notation KI Friction and a
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Part 2 Application
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9 by Erik B. Fiske BW/JP Internatio
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Vertical Pumps 115 Figure 9-2. Well
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Vertical Pumps 117 Figure 9-4. Subm
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Vertical Pumps 119 Figure 9-6. Inst
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Vertical Pumps 121 Figure 9-8. Barr
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Vertical Pumps 123 • Loading pump
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Vertical Pumps 125 Wet Pit Pumps Th
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Vertical Pumps 127 • Fresh water
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Vertical Pumps 129 Condensate and H
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Vertical Pumps 131 mally insulate w
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Vertical Pumps 133 Figure 9-15. Imp
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Vertical Pumps 135 checked for corr
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Vertical Pumps 137 crating paramete
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10 Pipeline Pipe line, Waterflood,
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Pipeline, Waterflood and CO 2 Pumps
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Pipeline, Waterfiood and CO 2 Pumps
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Figure 10-11. Performance change wi
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Figure 10-13. Seven-stage pump dest
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Pipeline, Waterflood and COa Pumps
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11 By Edward Gravelle Sundstrand Fl
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High Speed Pumps 175 History and De
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High Speed Pumps 177 Figure 11-2. (
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High Speed Pumps 179 some portion o
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High Speed Pumps 181 This is to say
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High Speed Pumps 183 This expressio
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High Speed Pumps 185 Figure 11-3. P
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High Speed Pumps 187 As an aside, p
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High Speed Pumps 189 Figure 11-5. I
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High Speed Pumps 191 Figure 11-7. I
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High Speed Pumps 193 Figure 11-9. R
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High Speed Pumps 195 Figure 11-10.
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High Speed Pumps 19? Figure 11-11.
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High Speed Pumps 199
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High Speed Pumps 201 Figure 11-13.
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High Speed Pumps 203 nal bearings a
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High Speed Pumps 205 Barske, U, M.,
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Double-Case Pumps 207 jected to ext
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Double-Case Pumps 209 Figure 12-3.
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Double-Case Pumps 213 ally by split
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Double-Case Pumps 215 The throttle
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Figure 12-11. pump for 4,000 psi In
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Double-Case Pumps 219 so that the t
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Doubte-Case Pumps 223 Volute Casing
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Double-Case Pumps 225 5. Survey of
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Slurry Pumps 227 An approximate com
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Slurry Pumps 229 Figure 13-2. Nomog
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Slurry Pumps 231 Table 13-2 Alloys
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Slurry Pumps 233 Figure 13-3. Class
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Figure 13-4, (A) (B) (C)
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Slurry Pumps 237 There is little to
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Figyre 13-7, (courtesy Pumps, Inc.)
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Flgyr« 13-8, with (courtesy Goulds
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Slurry Pumps 243 ing the pump speed
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Slurry Pumps 245 Where there exists
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Hydraulic Power Recovery Turbines 2
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Figure 14-14. Internally adjustable
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14-22, Flow of hydraulic recovery a
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15 by Frederic W. Buse Ingersolf-Ra
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Chemical Pumps Metallic and Nonmeta
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Driver Chemical Pumps Metallic and
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Part3 Mechanical Design
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16 Shaft Design and Axial Thrust Sh
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Shaft Design and Axial Thrust 335 S
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Shaft Design and Axial Thrust 337 W
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Shaft Design and Axial Thrust 339 T
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Shaft Design and Axial Thrust 341 b
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Shaft Design and Axial Thrust 343 K
Page 360 and 361: Double-Suction Single-Stage Pumps S
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Page 368 and 369: D (with subscript) P D P s T T (wit
Page 370 and 371: Mechanical Seals 355 Figure 17-1. M
Page 372 and 373: Mechanical Seats 357 Figure 17-2B.
Page 374 and 375: Mechanical Seals 359 Figure 17-2D.
Page 376 and 377: Mechanical Seals 361 Figure 17-4. H
Page 378 and 379: Mechanical Seals 363 Pressure-Veloc
Page 380 and 381: Mechanical Seals 365 The temperatur
Page 382 and 383: Mechanical Seals 367 Figure 17-7. B
Page 384 and 385: Mechanical Seals 369 Figure 17-9. P
Page 386 and 387: Mechanical Seals 371 where C 3 = 53
Page 388 and 389: Mechanical Seals 373 Classification
Page 390 and 391: Mechanical Seals 375 Double seals m
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Page 394 and 395: Mechanical Seals 379 Figure 17-19.
Page 396 and 397: Mechanical Seals 381 Table 17-4 Tem
Page 400 and 401: Mechanical Seats 385 steam, is to p
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Page 404 and 405: Mechanical Seals 389 Mechanical Sea
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Page 412 and 413: Mechanical Seals 39? Figure 17-34.
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Page 418 and 419: Mechanical Seals 403 alignment, par
Page 434 and 435: Mechanical Seats 419 Figure 17-58.
Page 436 and 437: Vibration and Noise in Pumps 421 Re
Page 438 and 439: Vibration and Noise in Pumps 423 me
Page 440 and 441: Vibration and Noise in Pumps 425 in
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Page 444 and 445: Vibration and Noise in Pumps 429 ot
Page 446 and 447: Vibration and Noise in Pumps 431 Fi
Page 448 and 449: Vibration and Noise in Pumps 433 fi
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Page 452 and 453: Vibration and Noise in Pumps 437 up
Page 454 and 455: Vibration and Noise in Pumps 439 Fi
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Vibration and Noise in Pumps 445 Fi
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Vibration and Noise in Pumps 453 Re
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Vibration and Noise in Pumps 457 Ac
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Vibration and Noise in Pumps 461 As
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Vibration and Noise in Pumps 463 ci
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Vibration and Noise in Pumps 467 sp
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Vibration and Noise in Pumps 469 Be
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Vibration and Noise in Pumps 475 Vi
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Vibration and Noise in Pumps 489 pe
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Vibration and Noise in Pumps 491 th
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Vibration and Noise in Pumps 4S3 fo
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Part 4 Extending Pump Life
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19 by Malcolm G. Murray, Jr. Murray
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Alignment 499 Figure 19-2. Pump dam
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Alignment 501 The best designs fail
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Table 19-1 Vertical Alignment Movem
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Table 19-2 Continued Horizontal Ali
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Alignment 507 bearing motors becaus
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Alignment 509 meet results. It shou
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Alignment 511 Determination of Tole
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Table 19-3 Continued Primary Alignm
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Alignment 515 Figure 19-3 A & B. Tw
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Table 19*4 Continued Methods of Cal
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Alignment 510 parallelism/perpendic
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Alignment 521 Table 19-5 continued
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Alignment 523 3. Essinger, J. N., B
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Rolling Element Bearings and Lubric
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Roiling Element Bearings and Lubric
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Roiling Element Bearings and Lubric
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Failure Analysis Mechanical Seal Re
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Table 21-2 Causes of Seal Failures
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Mechanical Seal Reliability 561 ^mi
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Mechanical Seal Reliability 563 Sea
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Mechanical Seal Reliability 565 run
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Reliability Mechanical Seal Reliabi
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Index A thermal growth, 519-522 ver
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Critical speed analysis. See also V
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Index 573 inlet angle, 37 classific
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Index 575 Shaft design, 333-343 ind
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double, 52-54 velocity ratio, 50-51
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Centrifugal Pumps Design and Application 2nd ed - Val S. Lobanoff, Robert R. Ross (Butterworth-Heinemann, 1992)

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